Bearing



FgbpZl, 1939. A. G; F! WALLGREN ,1 BEARING Filed Sept. 7, 1935 4 Sheets-Sheet 1 7f INVEZZOR.

, ATTORNEY.

Feb. 21, 1939- A. e. F. WALLGREN BEARING Filed Spt. 7, 1955 4 Sheets-Sheet 2 Feb. 21, 1939. G F, W LLGREN 2,148,144

BEARING Filed Sept. 7, 1935 4 Sheets-Sheet 3 INVENTOR.

1 qATTORNEY.

BEARING Filed Sept. 7, 1935 4 Sheets-Sheet 4 INVENTOR.

. 4 1 ATTORNEY.

Patented Feb. 21, 1939 UNITED STATES PATENT OFFICE Sweden, assignor, by mesne assignments, to Aktieboiaget Nomy, Lidkoping, Sweden, a. corporation of Sweden Application September 7, 1935, Serial No. 39,533 In Sweden September 12, 1934 27 Claims.

My invention relates to bearings and more particularly to a combined radial and thrust bearing.

One of the objects of my invention is to provide a bearing of this type in which the thrust loads have no eifect on the bearing surfaces designed to carry radial loads, but such thrust loads are taken entirely by thrust bearing members. Another object of my invention is to provide improved means for lubricating a bearing of this type.

Still further objects of my invention are to provide improved lubricant sealing means for preventing escape of lubricant from the bearing and to provide means for preventing accumulation of lubricant foam on the surface of the lubricant in the bearing housing.

Still another object of my invention is to provide a bearing of this type which may be mounted in standard bearing housings without requiring any alterations of the latter.

Further objects and advantages of my invention will be apparent from the following description considered inconnection with the accompanying drawings which form a part of this specification and of which:

Fig. 1 is a cross-sectional view of one embodiment of my invention, and is taken on the line II of Fig. 2;

Fig. 2 is a cross-sectional view taken on the line 2--2 of Fig. 1;

Fig. 3 is a cross-sectional view of a portion of the bearing and is taken on the line 33 of Fig. 2;

Fig. 4 is a view, partially in crosssec tion, of a bearing member shown in Figs. 1 through 3;

Fig. 5 is an end view of a Garden ring employed in the bearing; 4

Fig. 6 is a cross-sectional view taken on the line 6-6 of Fig. 5;

Fig. 7 is a cross-sectional view, similar to Fig. 3, of a portion of a bearing in accordance with a second embodiment of my invention;

Fig. 8 is an end view of a part of the bearing shown in Fig. 7;

Fig. 9 is a cross-sectional view of a third embodiment of my invention;

Fig. 10 is a cross-sectional view of the bearing shown in Fig. 9 and shows lubricant passages;

- Fig. 11 is a cross-sectional view of a bearing similar to that shown in Fig. 1 but with diiferent lubricating means;

Fig, 12 is a partial view of a bearing member shown in Fig. 11; I

Fig. 13 is a cross-sectional view of the bearin member showing a slightly different embodiment of my invention;

Fig. 14 is a cross-sectional view of a still further embodiment of my invention;

Fig. 15 is a cross-sectional view taken on the line Iii-I5 of Fig. 14;

Fig. 16 is an end view of the bearing shown in Fig. 14; and

Fig. 17 is a cross-sectional view of still another embodiment of my invention.

Referring more particularly to Figs. 1 through 6, reference character I0 designates a rotatable shaft subjected to both radial and thrust loads. Rigidly secured to shaft III in any suitable manner, as by shrinking, is rotatable bearing member II. Member II is formed with a cylindrical radial bearing surface I2 and oppositely disposed plane thrust bearing surfaces I3. Concentric with member II is a rotationally stationary radial bearing member I4 having a cylindrical bearing surface I5 cooperating with the bearing surface I2 on member II. By reason of'the grooves I6 in member I 4, the bearing surface I5 has less axial extent than the bearing surface I2 on member II. This permits axial displacement of the two members within limits without altering the area of the operative bearing surfaces.

Bearing member I 4 is formed with a centrally located outwardly extending annular projection I1, the periphery of which is formed as a ,curved surface I8. This curved surface is preferably spherical or barrel-shaped. Surface I8 on the loaded side of the bearing rests on the inner cylindrical surface of a bearing housing I9. This permits tilting of member I4 in case shaft I0 is slightly out of alignment. Projection I1 is formed with a recess 20 which receives a key I-9a received in housing I9 which prevents rotation of member I4 with respect to the housing.

Disposed on either side of bearing members I I and I4 are hood members 2|. Secured within the hood members, as by spot-welding, are thrust bearing rings 22 having thrust bearing surfaces 23 cooperating with the thrust bearing surfaces I3 on member II. Hood members 2| are formed with axially extending flanges 24 which are disposed between bearing member I4 and the bearing housing. Radially extending flanges 25 are formed on axial flanges 24 and lie adjacent to the projection I! on, bearing member I4. The hood members on the opposite sides of the bearrality of pins 26 extending freely through aper tures 21 formed in bearing member I4. In the bearing member I. Hood members 2| are fur.-.

ther connected together by means of pins 29 which are secured to flanges 25 and extend through recesses 30 formed in projection ll of bearing member ll. It will be noted that pins 26 and 29 are of such length that flanges 25 are spaced a distance from projection IL This di stance determines the'amount of axial displacement possible between the hood members and the on the hood members.

hearing member l4. Hood members 2| are supported within housing L9 by means of Cardan rings ll. As shown more particularly in Figs. 5 and 6, Garden rings 3| are formed with diametrically opposed projections 32 on one side thereof which bear against flanges Disposed at from projections 32, and on the opposite side of ring 3|, is a pair of similar projections 55. These projections bear against a face 30 formed within bearing housing l9. Cardan rings 3| permit universali movement of the hoods 2|, and consequently of thrust bearing members 22, withrespect to the bearing housing. This equalizes the thrust pressure around rings 22 in case of any misalignment of the shaft. I

The bearing surface l2 of member II is formed with a diagonally extending groove 55 which serves to permit the entrance of lubricant between the bearing surfaces which lubricant, upon rotation of member N, forms a film between the bearing surfaces. This film serves to prevent metal-to-metal contact and transmits radial load between the surfaces. In order to supply lubricant to the radially inner periphery of the thrust bearing surfaces It and 23, rings 22 are formed with a plurality of passages 40. These passages are distributed around rings 22 so that, regardless of the mounting of the bearing, some of these passages will be below the surface of the lubricant in housing I9. Hoods 2| are formed with radially extending flanges 4| which lie closely adjacent to the end surface of bearing member Inasmuch as the hood members are displaced axially with the bearing member I, the spaces between flanges 4| and the bearing member remain constant. Flanges ll cooperatewith the bearing member to form a lubricant seal which prevents the escape of lubricant to the shaft "I, along which it might be ber II and serve to permit any lubricant which is in the upper part of the bearing when rotation ceases, to return to the lower part.

If desired, thrust rings 22 may be omitted and housings 2| may be formed with thrust bearing surfaces directly thereon cooperating with the thrust bearing surfaces I! on member The operation of the above described bearing is as follows:

Radial load acting on shaft I5 is transmitted through bearing member H to the lubricant fllm maintained between the radial bearing surfaces l2 and I5. This fllm int-turn transmits the radial load to bearing member II which is supported within the bearing housing. In the event that the shaft is out of alignment and hence .wobbles slightly, bearing member I may'follow this wobbling movement by tilting on curved sur- 5 face It. This prevents any undue concentration of pressure at one edge of the radial bearing. If the shaft I0 is subjected to thrust loads, such load is. transmitted through the member II to one or the other of the thrust bearing surfaces l3, 1( from whichit is transmitted through the oil fllm to the corresponding thrust ring 22. From here the thrust is carried by the hood member 2| to the Cardan ring 3| and is finally absorbed by the bearing housing l9. Again, in case of a mis- Y alignment of the shaft, Cardan rings 3| enable the thrust bearing rings 22 to follow the wobbling of member II. This results in an equal distribution of load around the entire bearing face of the ring. 2( The imposition of-thrust on shaft It causes a slight axial displacement of this shaft, butthis has no effect on the radial bearing surfaces l2 and I5 except to displace surface I! slightly with respect to surface l5. It in no manner alters the radial load carried by the surfaces. Due to the fact that surface l5 has a slightly different extent than the surface l2, axial displacement of these surfaces may take place without changing the areas thereof available to transmit radial 3i loads. i

It will thus be seen that both the rotatable bearing' member H and the stationary thrust bearing structure including hoods2| and rings 22 are displaceable axially with respect to the stationary radial bearing member ll. It will be understood that this axial displacement is very slight and results from slight deformations of the parts. However, this is sufficient so that if it were allowed to act on the radial bearing surfaces it would have 4 a serious adverse effect upon the lubricant film maintained therebetween.

In Figs. '7 and 8 there is shown another embodiment of my invention. In the bearing showing in these figures, the bearing member II is 4 secured to shaft III by means of a conical clamping sleeve 55 and a clamping nut 55, the latter being locked by a lock washer 51. Member II is provided with an axial extension 45 against which the nut it bears. The presence of this 5 extension necessitates a change in the shape of hood member 2 la on this side of the bearing. Asshown, the hood member is formed with an axially extending flange 45 which lies parallel with and closely adjacent extension 45. There is also 5 provided a hood 55 for covering lock-nut 55 in order to prevent agitation of the oil by the rotation of the nut. Hood 5|] is secured to hood member 2|a by means of a nut 5| threaded on a pin 52 which is secured to hood member 2|a. a Pin 5| extends through a bayonet slot 55 in hood 50, the larger end of the slot being of sufilcient diameter to accommodate nut 5|. This makes attachment and removal of hood 55 easy when it is desired to gain access to lock-nut 45. Othera wise, the construction and operation of this modiflcation is the same as that disclosed in Figs. 1 through 6, wherefore further explanation is not believed to be necessary.

In the embodiment shown in Figs. 9 and 10, the 7 hood members are replaced by sleeve thrust rings 55 and 56 secured together by means of pins 51 which extend through apertures 21 in bearing member I4. The thrust rings are formed with radial projections 58 having radial surfaces 59. 7

- the thrust is transmitted through pins 51 to the Cardan rings 3| are disposed between surfaces bodiment the key is located at the top of the 59 and inwardly extending annular projection 80 formed in the bearing housing. Projection 50 also serves to support projection II on bearing member I4.

An annular disc M is secured to bearing ring 55 and extends close to the shaft. A hood member 62 is secured to bearing ring 56 and encloses lock nut 46.

Lubricant is supplied to the radial and thrust bearing surfaces by means of passages 88 formed in the thrust rings 55 and 56. In this embodiment, the thrust bearing surface 84 on ring II is wave-shaped as is indicated by the dotted line 65. The rotation of this wave-shaped surface serves to create and maintain a lubricant film between it and the cooperating surface.

The operation of this bearing, in so far as radial loads are concerned is similar to that described above. With respect to thrust loads there is a slight diflerence due to the different arrangement of the Cardan rings. A thrust load actin in the direction of the arrow in Fig. 9 is transmitted from bearing member II to thrust ring 55 on the, left-hand side of the bearing. From here thrust ring 58 on the other side of the bearing. Thence the thrust is transmitted through the Cardan ring cooperating with thrust ring 56 to the annular projection 60 on the bearing housing.

The embodiment shown in Figs. 11 and 12 differs from that shown in Figs. 1 through 6 in the manner in which lubricant is supplied to the radial bearing surfaces. Bearing member II is formed with annular recesses I0 in its end faces. These recesses are preferably conical and extend from the end faces toward the radial bearing surface I2. From these recesses lubricant ducts II lead to a recess 12 formed in the central part of bearing surface I2. As shown in Fig. 12 recess I2 may be disposed obliquely, in a manner similar to recess 35 shown in Fig. 4. However, recess I2 does not extend entirely across the face of the bearing. In the modification shown in Figs. 11 and 12, ducts II communicate with opposite ends of recess I2 while in the modification shown in Fig. 13 the ducts II meet at the center of recess 12a.

In operation, lubricant is supplied to the space radially within thrust rings 22 through the passages 40 and this lubricant serves to lubricate thrust bearing surfaces as well as flowing into annular recesses I0 in bearing member II. The rotation of bearing member II causes centrifugal force to cause flow of lubricant from recesses I0 through ducts II to recess 12. This flow takes place continuously and even while the duct II and recess I2 are above the level of the lubricant in the bearing housing. This assures a continuous and adequate supply of lubricant to the radial bearing surfaces.

In the embodiment shown in Figs. 14 through 16, reference character I0 again designates a rotatable shaft to which is rigidly secured the rotatable bearing member II. Member II is formed with a cylindrical radial bearing surface I2 and oppositely disposed thrust bearing surfaces I3. The stationary radial bearing member I4 is mounted within bearing housing I9 in a. manner similar to that described in connection with the bearing shown in, for instance, Fig. 1. Rotation of member I4 with respect to housing I9 is prevented by means of a key 80 received within a slot 8| formed in the periphery of the annular projection IT on the bearing member. In this emvare in alignment.

bearing instead of at the bottom.

' Hood members 83 are disposed on either side of the bearing members II and I4 and are provided with thrust rings 84 having thrust bearing surfaces cooperating with the surfaces I3 on member II. Hoods 83 are formed with inner axial flanges 85 having a diameter substantially the same as that of the inner diameter of rings. 84. Flanges 85 center the rings 84 with respect to the hood members and ridges 86 formed in flanges 85 enter into recesses 81 in the rings 84 and prevent relative rotational movement between the rings and the hoods.

Hoods 83 are also formed with outer axial extending flanges 88 integral with which are radially extending flanges 89. Flanges 89 on the two hood members are connected together by means of a plurality of pins 90 which extend through recesses 9| formed in projection I! of bearing member I4. Flanges 89 are spaced apart a distance which is slightly greater than the width' of annular projection I1, whereby axial displacement of the hoods with respect to bearing member I4 is permitted.

Inner hood members 92 are secured within hood members 83 and have axially extending portions which overlap the ends of bearing member I4 with a certain amount of play so as to permit the flow of lubricant therebetween. I

Spring-retaining rings 93 are disposed on opposite sides of bearing member I4 and are held in contact therewith by means of circular springs 94 which are bent in the manner shown in Fig. 14 so that diametrically opposite points contact rings 93 while other diametrically opposite points disposed at substantially 90 thereto contact the inner hood members 92. These springs are placed in the same relative position as are springs 28 shown in Fig. 1 and serve the same purpose, namely, to center bearing member I4 during assembly and to tend to maintain it in a proper position during'operation of the-bearing. The springs 94 are preferably on assembly given an initial tension.

Bearing member II is formed with annular recesses 95 with which communicate channels 98 leading to the cylindrical bearing surface I2. Inner axial flanges 85 of the hood member ex tend within recesses 95 and form lubricant seals 95a. Cup-shaped members 91 are secured within flanges 85 and are provided with radially extending flanges 98 which are disposed closely adjacent to the end surfaces of bearing member II, thereby providing lubricant seals 99 therebetween.

Each of hood members 83 is formed with an opening I00 in the lower part thereof and preferably a plurality of openings I 0| in the upper part thereof. Inner hood member 92 is formed with an opening I02 in alignment with opening I00. Wings I03 are formed at the ends of opening I00 and these wings extend into openings I02 and this assures that openings I00 and I02 H'ood members 83v are provided with further openings I04 in the lower part thereof which communicate with openings I05 formed in ring members 84, which openings I05 lead to annular recesses 95, whereby lubricant is supplied from outside of hood members 83 to the bearing surfaces.

Cardan rings I06 are disposed between flanges 89 on hood members 83 and annular projections I01 are formed within the bearing housing in a manner similar to that disclosed in the bearing shown in Fig. 1. The bearing above described, and shown in Figs. 14 through 16, acts in a similar manner to the bearings previously described in so far as transmission of radial and thrust loads is concerned. As above indicated, lubricant is supplied to annular recesses 95 through openings I04 in the hood members and through openings I in thrust rings 84. From here lubricant is supplied by centrifugal force through passages 86 to the radial bearing surfaces. Lubricant is also supplied from recesses 85 to the thrust bearing surfaces. the bearing are enclosed within inner hood members 92 oil and oil foam produced by agitation of the oil is prevented from being freely thrown out by centrifugal force to the annular space between hood members 88 and stationary bearing member l4. Oil thus enters that space in an even flow and from there the oil passes out throughopenings I00 which are below the oil level to the outer bearing housing. I have found that oil foam does not accumulate on the surface of the lubricant in the bearing housing proper where it might otherwise accumulate especially at high revolutions until it reached the rotating 'shaft to which it would adhere and possibly be carried out of the bearing housings Without the inner hood members 92 a rotating ringv of oil and oil foam might be formed also in the annular space between hood members 88 and bearing member l4 and in this way restrain an equalization of the oil level on opposite sides of the bearing through openings Hill in hoods 88.

Passage of lubricant from recesses 95 to the shaft I0 is prevented by the lubricant seals95a and 99. The openings I Iii in the upper part of hoods 83 provide for an equalization of pressure on opposite sides of the bearing.- Unequal pressure might be built up if the bearing were used in a machine having a fan which produced an axially directed flow of air. If not equalized, this pressure difference would result in a difference in the level of the lubricant on opposite sides of the bearing and might force the level up on one side until the lubricant contacted the shaft.

The embodiment shown in Fig. 1'1 differs from that shown in Figs. 14 through 16" chiefly in the ber 83 at this side of the' bearing is not provided with a cup-shaped member 81 as is the hood on the other side, but a shield I I3 which covers nut I I! may be secured thereto by means of a threaded pin I I4 and nut III in much the same manner as disclosed in Fig. 7.

Sleeve H0 is split as is shown at I16 in order to be resilient for clamping purposes, The resulting axially extending groove is apt to collect lubricant, particularly when the bearing is rotating at low speeds so that centrifugal force does not act to prevent the flow of lubricant through seal 89. In order to prevent this lubricant from flowing to the shaft ID, the sleeve is formed with an unsplit extension H1 and an annular groove H8. Thus any lubricant flowing axially through the slit in sleeve 0 flows into Inasmuch as all of the rotating parts of an oil lock for lubricant flowing through the slit in the sleeve in this direction.

It is not believed that a further description of the operation of the bearing shown in Fig. 17 is necessary as it operates in a manner similar to Figs. 14 through 16 with the exceptions above noted,

While I have shown and described several embodiments of my invention, it is to be understood that this has been done for purposes of illustration only and that further embodiments, and modifications thereof, fall within its scope, which is limited only by the appended claims when considered in connection with the prior art.

I claim:

1. In a combined radial and thrust bearing, means providing rotatable radial bearing surface and rotatable thrust bearing surface, a first rotationally stationary member formed with radial bearing surface, and a rotationally stationary hood member disposed at one side of said means and formed with thrust bearing surface and having a portion spaced axially closely to said means ?to form a lubricant seal therewith, said means being axially displaceable together with said hood member with respect to said first member, whereby the space between said hood and said means is maintained substantially constant.

2. In a. combined radial and thrust bearing, a rotatable bearing member formed with radial bearing surface and oppositely disposed thrust bearing surfaces, a rotationally stationary radial bearing member cooperating with the rotatable radial bearing surface, and rotationally stationary hood members enclosing said rotatable bearing member and formed with thrust bearing surfaces cooperating with the rotatable thrust bearing surfaces and having portions spaced closely to said rotatable bearing member to form lubricant seals therewith, said rotatable bearing member being axially displaceable together with said hoods with respect to said stationary radial bearing member, whereby the spg between said portions and said rotatable bearing member are maintained substantially constant.

3. In a combined radial and thrust bearing, a rotatable bearing member formed with radial bearing surface and oppositely disposed thrust bearing surfaces, a rotationally stationary radial bearing member cooperating with the rotatable radial bearing surface, rotationally stationary hood members disposed on either side of said rotatable bearing member and provided with thrust bearing surfaces cooperating with the rotatable thrust bearing surfaces, and means for securing said hood members together, said rotatable bearing member and said hood members being axially movable independently of said stationary radial bearing member.

4. In a combined radial -and thrust bearing, a stationary bearing support, a rotatable bearing member formed with radial bearing surface and oppositely disposed thrust bearing surfaces, a rotationally stationary radial bearing member co-' operating with the rotatable radial bearing surface, rotationally stationary thrust bearing members cooperating with the rotatable thrust hearing surfaces, said rotatable bearing ember and said stationary thrust bearing members being 'ing member.

thrust members to said bearing support lnde pendentiy of said resilient means.

5. In a combined radial and thrust bearing, a rotatable bearing member formed with radial bearing surface and oppositely disposed thrust bearing surfaces, a rotationally stationary radial bearing member cooperating with the rotatable radial bearing surface, rotationally stationary hood members disposed on either side of said rotatable bearing members and provided with thrust bearing surfaces cooperating with the rotatable thrust bearing surfaces, means for securing said hood members together, said rotatable bearing member and said hood members being axially movable with respect to said stationary radial bearing member, and resilient means-between said hoodmembers and said stationary radial bearing member.

6. In a combined radial and thrust bearing, a housing, a rotatable bearing member having radial bearing surface and oppositely disposed thrust bearing surfaces, a rotationally stationary radial bearing member cooperating with the 'rotatable radial bearing surface, the last mentioned member being formed with a. spherical supporting surface for rockably mounting said last mentioned member in said housing, rotationally stationary thrust bearing members cooperating with the rotatable thrust bearing surfaces, said rotatable bearing member and said stationary thrust bearing members being axially movable with respect to said stationary radial bearing member, and spring means between said stationary thrust bearing members and said stationary radial bear- 7. In a combined radial and thrust bearing, a housing, a rotatable bearing member having radial bearing surface and oppositely disposed thrust bearing surfaces, a rotationally stationary radial bearing member cooperating with the rotatable radial bearing surface, the last mentioned member being formed with an annular outwardly extending centrally located projection having a,

with thrust bearing surfaces cooperatingwith the rotatable thrust bearing surfaces, said hood members enclosing said stationary radial bearing member and being formed with flanges spaced slightly from said annular projection, and means securing said hood members together, said rotatable bearing member and said hood members being movable axially with respect to said stationary radial'bearing memberan amount determined by the spacing of said flanges from said projection.

8. In a combination radial and thrust bearing, a housing, a rotatable bearing member having radial bearing surface and oppositely disposed thrust bearing surfaces, a rotationally stationary radial bearing member cooperating with the rotatable radial bearing surface and formed with an outwardly extending annular projection for supporting said stationary bearing member in said housing, rotationally stationary hood members disposed on either side of said rotatable bearing member and provided with thrust bearing surfaces cooperating with the rotatable thrust bear-.

ing surfaces, portions of said hood members extending within the space between said stationary bearing member and said housing on either side of said projection, and universal movement means for supporting said hood members from said housing disposed in said space.

9. In a combination radial and thrust bearing, a rotatable bearing member having radial bearing surface and oppositely disposed thrust bearing surfaces, a rotationally stationary radial bearing member cooperating with the rotatable radial bearing surface, rotationally stationary hood members disposed on either side of said rotatable bearing member and rings secured to said hood members and formed with thrust bearing surfaces cooperating with the rotatable thrust bearing surfaces, said rings being formed with passages for admitting lubricant to the radially inner parts of said thrust bearing surfaces.

10. In a bearing, a rotatable member having a bearing surface, a rotationally stationary member having a bearing surface, said rotatable member being axially displaceable with respect to said rotationally stationary member, a hood disposed at the side of said members and defining a lubricant chamber adjacent to said bearing surfaces, said hood having a portion spaced axially closely to said rotatable member to form a lubricant seal therewith, and means for mounting said hood so that it is rotationally stationary with respect to said rotationally stationary member and is displaceable axially together with said rotatable member, whereby the axial space between said hood and said rotatable member is maintained constant.

11. In a bearing, a rotatable member having a bearing surface, a rotationally stationary member having a bearing surface, said rotatable member being axially displaceable with respect to said rotationally stationary member, a hood disposed at the side of said mem and defining a lubricant chamber adjacent to said bearing surfaces, said hood having a portion spaced axially closely to said rotatable member to form a lubricant seal therewith, means for mounting said hood so that it is rotationally stationary with respect to said rotationally stationary member and is displaceable axially together with said rotatable member, whereby the axial space between said hood and said rotatable member is maintained constant, and means for restraining said hood against radial movement with respect to both of said members.

12. In a combined radial and thrust bearing, a rotatable member having radial bearing surface at the periphery and thrust bearing surface at the end thereof, a rotationally stationary member having radial bearing surface, a hood disposed at the side of said members and provided with thrust bearing surface, said hood forming a lubricant chamber adjacent to said bearing surfaces and having a portion spaced closely to said rotatable member to form a lubricant seal therewith, and means for mounting said hood so that it is axially displaceable with said rotatable member and with respect to said rotationally stationary member.

13. In a bearing, a rotatable member having a bearing surface, a rotationally stationary member having a bearing surface, said rotatable member being axially displaceable with respect to said rotationally stationary member, a hood disposed at the side of said members and defining a lubricant chamber adjacent to said bearing surfaces, said hood having a portion spaced axialsaid hood and said rotatable member is main-- tained constant, said rotatable member being formed with an annular groove radially outside said lubricant seal to provide a drain for lubricant from the upper part of said bearing.

14. In a bearing, a housing forming a lubricant reservoir, a rotatable bearing member, a rotationally stationary bearing member, a rotationally stationary outer hood enclosing said members within said housing, said hood being formed with a passage for the flow of lubricant from said housing to the bearing surfaces of said members, and a rotationally stationary inner hood between said outer hood and said members arranged to prevent access of lubricant foam produced by the rotation of said rotatable member to the lubricant in said reservoir,

15. In a bearing, a housing forming a lubricant reservoir, a rotatable bearing member, a rota tionally stationary bearing member, a rotationally stationary outer hood enclosing said members within said housing, said hood being formed with a passage for the flow of lubricant from said housing to the bearing surfaces of said members, and a rotationally stationary inner hood defining a space between said outer hood and said rotatable member and arranged to prevent lubricant agitated by the rotation of said rotatable member from being freely thrown out from said space, said hoods being formed with communicating passages for the flow of lubricant from said space to said reservoir.

,16. In a bearing, a housing forming a lubricant reservoir, a rotatable bearing member, a rotationally stationary bearing member, a rotationally stationary outer hood enclosing said members within said housing, said hood being formed with a passage for the flow of lubricant from said housing to the bearing surfaces of said members, and a rotationally stationary inner hood defining a space between said outer hood and said members and arranged to restrict agitation of oil by said rotatable bearing member to said space, said inner hood having a loose fit with said stationary bearing member whereby liquid lubricant may flow therebetween.

17. In a bearing, a housing forming a lubricant reservoir, a rotatable bearing member, a rotationally stationary bearing member, a rotationally stationary outer hood enclosing said members, said rotatable member being formed with an annular groove in the end thereof and a lubricant duct connecting said groove with the bearing surface on said rotatable member, said hood being formed with a passage for the flow of lubricant from said reservoir to said groove, and a rotationally stationary inner hood between said outer hood and said members arranged to prevent access of lubricant foam produced by rotation of said rotatable member to the lubricant in said reservoir.

18. In a combined radial and-thrust bearing, a housing forming a lubricant reservoir, a rotatable member having radial and thrust bearing surfaces, a rotationally. stationary member having radial bearing surface, a rotationally sta: tionary outer hood enclosing saidmembers, said hood being provided with a thrust bearing surface and being formed with a passage for flow of lubricant from said reservoir to said bearing surfaces, and a rotationally stationary inner hood between said outer hood and said members and radially beyond the thrust bearing surfaces, said inner hood being arranged to prevent access of lubricant foam producedby the rotation of said rotatable member to the lubricant in said reservoir. A

19. In a combined radial and thrust bearing, a housing forming a lubricant reservoir, a rotatable member having radial and thrust bearing surfaces, a rotationally stationary member having radial bearing surface, a rotationally stationary outer hood enclosing said members, said hood being provided with a thrust bearing surface, said rotatable member and said hood being axially displaceable with respect to said rotationally stationary member, said hood being formed with a passage for flow of lubricant from said reservoir to said bearing surfaces, and a rotationally stationary inner hood between said outer hood and said members and radially beyond the thrust bearing surfaces, said inner hood being arranged to retain lubricant foam produced by the rotation of said rotatable member and to prevent access of said foam to the lubricant in said reserk voir.

20. In a bearing, a rotatable'ring member for mounting on a shaft, a rotationally stationary ring member for mounting in a bearing housing, said members having bearing surfaces, and rotationally stationary hood members on either side of said rotatable member, said hood member and said rotatable members being axially displaceable with respect to said rotationally stationary ring member.

21. In a combined radial and thrust bearing, a stationary bearing support, means providing rotatable radial bearing surface and rotatable thrust bearing surface, a rotationally stationary element formed with radial bearing surface, and a rotationally stationary hood member disposed at one side of said means and formed with thrust bearing surface, and having a portion spaced closely to said means to form a lubricant seal therewith, said hood member being axially distherewith, and means for transferring thrust from said hood member to said bearing support independently of said rotationally stationary element.

23. In a sliding friction bearing for a substantially horizontal shaft, a bearing housing forming a lubricant reservoir, an outer stationary bearing ring supported in said housing, an inner rotating ring adapted to be secured to the shaft, said rings having cooperating sliding bearing surfaces, a rotationally stationary hood disposed on one side of said rings and provided with a thrust bearing surface, said inner ring having cooperating-thrust bearing surface, said hood having an opening below the level of the lubricant in said reservoir to provide communication between the reservoir and the space within said hood radially within said sliding surfaces, the lateral face of said inner ring adjacent to said hood member being formed with a recess extending axially in-' wardly and radially outwardly to thereby form a pocket which, on rotation of the inner ring, picks til up lubricant on passing below the level of the lubricant in the reservoir, and a channel in said inner ring extending from said recess to said cooperating sliding bearing surfaces.

24. In a combined radial and thrust bearing, a housing, a rotationally stationary bearing member mounted in said housing, a rotatable bearing member, said bearing members having cooperating radial bearing surface, said rotatable bearing member being formed with thrust bearing surface on a lateral face thereof, a hood member made of deformable sheet metal disposed in said housing and axially spaced from said lateral face, and an annular stiffening ring secured within said hood member and formed with thrust bearing surface cooperating with the thrust bearing surface of said rotatable bearing member, said hood member being supported from said housin so that thrust is transmitted from said hood member to said housing.

25. In a combined radial and thrust bearing, a stationary bearing support, a rotatable bearing member adapted to be mounted on a shaft, said member being formed with cylindrical radial bearing surface on the outer periphery thereof and with annular thrust bearing surfaces on either end thereof, a rotationally stationary element supported in said bearing support formed with radial bearing surface cooperating with the radial bearing surface of said member, rotationally stationary hood members disposed on either side of said rotatable bearing member and formed with annular thrust bearing surfaces cooperating with the thrust bearing surfaces on said member, and means for transferring thrust from said hood members to said bearing support independently'of said bearing member.

26. In a bearing, a stationary bearing support, a rotatable bearing member formed with a radial bearing'surface, a rotationally stationary bearing element formed with radial bearing surface, said rotatable bearing member being axially displaceable with respect to said bearing support, anda rotationally stationary hood member disposed at one side of said bearing member and defining an inner lubricant chamber and having a portion spaced closely to said rotatable bearing member to form a lubricant seal therewith, said hood member being arranged with respect to said rotatable bearing-member so that the space between them remains substantially constant upon axial displacement of said rotatable bearing member.

27. A bearing as defined in claim 24 in which the thrust bearing surface on the annular ring has a wave shaped contour to facilitate the creation and maintenance of a lubricant film between the thrust bearing surfaces, the additional stifiness provided by said annular ring reducing deformation of said wave shaped surface. AUGUST GUNNAR FERDINAND WALIGREN. 

